Textile ironing press



/ Aug. 3, 1943. E. DAVIS 2,326,015

' TEXTILE IRONING PRESS Filed March 24, 1959 8 Sheets-Sheet 1 FIG.|

Q6. "Q3 EfO 69 ERNEST DAVIS Aug. 3, 1943. E. DAVIS 2,326,015

TEXTILE IRONING PRESS Filed March 24, 1939 8 Sheets-Sheet 2 FIG.2

'IIIIIA 'IIIII. 'IIIIII'IL'IJ INVENTOR ERNEST DAVIS ATTORNEY S Aug. 3, 1943.

FIG.6

E. DAVIS 2,326,015

TEXTILE IRONING PRESS Filed March 24, 1939 v 8 Sheets-Sheet 3 INVENTOR ERNEST DAVIS ATTORNEY Aug. 3, 1943. E. DAVIS TEXTILE IRONING PRESS 8 Sheets-Sheet 4 Filed March 24, 1959 FIG.9

new

INVENTOR ERNEST DAVIS *fi ATTORNEYS Aug. 3, 1943. E. DAVIS 2,326,015

TEXTILE IRONING PRES S Filed March 24, 1939 8 Sheets-Sheet 5 T 83 8| 13 e4 e2 flg K Ev 86 7/ I a 14% as ea E1 4 f so- 94 76 we,

INVENTOR ATTORNEYS Aug. 3, 1943. E. DAVIS TEXTILE IRONING PRESS Filed March 24, 1939 8 Sheets-Sheet 6 FIG. l2

INVEN TOR.

ERNE ST DAVIS BY W 5 MUD A TTORNEYS.

Aug. 3, 1943.

E. DAVIS TEXTILE IRONING PRESS Filed March 24, 1939 8 Sheets-$heet '7 ERNEST DAVIS ATTORNEYS.

Aug. 3, 1943. DAVIS 2,326,015

TEXTILE IRONING PRESS Filed March 24, 1939 8 Sheets-Sheet 8 FIG.I6.

II .A' 136 2 n2 E I :38 13o L I l I30 I14 1 I41 IN VEN TOR.

ERNEST DAVIS BY x 46W Patented Aug. 3, 1943 arm-am TEXTILE InoNrNo raises Ernest Davis, Syracuse, N; y assignorto The Prosperity Company, Inc., corporationof New York Application March 24, 1939, Serial i V 12' Claims.

This invention relates to pressing machines,

and more particularlyto anew and" useful textile ironing press and the like for use'in the pressfinishing of. apparel; clothing, suits, and fabrics.

' and improved scissors-type textile-ironing and pressing machine, so calledbecau'se of the up and. down arcuate movement of its upper ironing head pivoted. on an axis locatedin the rear oflanrl proximate the pressure planeof the1c0acting pressing elements or' jaws-of well known form,

Syracuse, N. Y., a

(or. se -st) generally called. the'heacl and buck. While one 1 or more preferred examples of movable upper head and stationary lower paddedbuck types of pressing machines are illustrated herein, the in vention 'may-be used. in connection with other types of jaw-motion presses;

The invention has for its "general object a pressing machingactu'ating mechanism including a'uniforrnly constant" output motor and motion transmi ting means operated thereby by which the static inertia of the press head, when open, is easily overcome and the headsetin motion without jar or shock, and quickly moved, through the greater part of its closing movement, to nearly closed position through a; long; quick acting, ratio leverage, and into final closed -lsition ough a low ratio leverage, in one contmuous uniform operation of the prime mover during the transfer frornthe closing and open am movements and during thetransfer from the high ratio to e low ratio during closing, and all without shocks, jars, or slamming.

More specifically; it has for its object a pressing machine in which the head closes me downand forward arcuate path with the final closing movement a short upright portion'of the arc of movement practically at a'right angle to the pressing plane or face of thelowe'r pressernent or buck, and the upright actuating er having: successive forward. lever movement and vertical pull link movement under the uniformly constant force of the motor, and first fulcrurns about'an axis located. near the lower enrl cf the lever sothat the motion thereof is transferred to the press head through the long arm offthe lever and. then'as the press closes, the lever moves about an axis at its upper end pull link only. when leverage ratio "by the motor a d and brings into action thelow ratio. leverage which forces, or pulls, the actuating lever downwardlyeubstantially vertically as a pull link, clamping the press'heaol practically rectilinearly through the upright portion of its arcuate path into final heavy pressure position to always deliver maximum pressure and compensateor follow up for such variables-asdiiferent thicknesses of the piecesjof Work, different thicknesses of compression of the pad on the buck, and settling or permanently setting of the pad.

it furtagier has for its objeotactuating mechanism or motion transmitting mechanism between the motor andthe head for holding the fulcrum of the lever from substantial swinging movement while the press head. is downward and forward portion of its arc of movement, and. means actuated by the lever during its swinging movement about an axis at its upper end. for. moving the lever downward as a the upright portion of its arc of movement.

It further'has for its object, actuating mechanism or-mo-tion transmitting mechanism between the motor the incluainga toggle which effects the final closing through the low l means for holding the toggle folrled or coclre. cluringfthe preliminary closing of the press to a point before final pressure is applied, and to ca so the-toggle to straighten during the swingin g movement of the lever thus apply heavy pressure through the stra gntening toggle while the lever acts as a pull link.

It-further has for its object an. arrangement of the actuating mechanism whereby the head carrying lever and the actuating lever therefor nested and streamlined, or whereby one is received within the otlie'rwnenthe pressis open or closed, particularly tlie'upper portions thereof above the table of the press and in the'rear of the buck, alsowhereby the actuating lever the carrying lever do notmove rearwarclly during the opening and closing movement totne rear of a vertical plane tangent to the rear- ,-st surface of the upper portion of the lever, tois feature being in the interest of economy in floor space, safety to persons that may be near the machine when in operation, and in the interest of appearance.

ther objects appear throughout the specification.

passing through the the is passing through 7 stroke to move the pensates for such conflicting problem factors as starting hehead from standstill, the increasing r'e istance of the counter-balancing springs as they stretch, the necessity of conserving the motor. stroke until the end, the requirement not to impact and hammer the buck pad, overcomingthe rapid build-up of spring-pad resistance once final jaw compression begins, and accomplishing these ends without carrying all the load 7 or thrust upon cam and roller bearing surfaces which is one convenient method employed here int-he control of the motion of the variable-stroke leverage of this invention. By test, it is now found that with a motor means of given size, about five times more jaw compression can be exerted on the work and pad with this new textile press than with presses of conventional form.

The drawings [With the foregoing and other objects in view, the accompanying drawings illustrate several principal examples of the invention, particularly three main forms of leverages, wherein certain modifications in form, proportion, and mode of operation may be made without departing from the principles andadvantages taught in this dislosure, and "wherein- I ironing head resisted by constantly varying V forces, reconci is carried.

Figure 9 is a fragmentary upper rear view showing the assembly of the ironing head with its arm and a lever constituting a part of the com- 7 pound leverage.

Figure 10 is a top or plan view of the head-carrying arm (also known-as the yoke) loo-king down upon Figure 9. Note the long single-bearing pin through the tines of the bifurcated arm, and also note a set of short twin-bearing pins outside the arm tines in axial alignment with the bearing holes into which they are adapted to fit.

Figures 9"and lOare to be read with other views in thedrawings, since all forms of the in Figures 1 through 7 show a first form of the invention in two of its simpler constructions. A low-power compound-motion leverage mechanism first closes the mova'olehead to initial position, 1. e., light contact with'tzie padding on the buck, whereupon a high-power heavy-pressure vention shown herein employ this same leverand-arm assembly with the ironing head. This assembly provides'a shielding means for closing the operating clearance between the arm and lever; it insures safety because a careless person if behind the press cannot get his hands in the mechanism, and it enhances the appearance of the straight simple lines of the press.

Figure 11 is a diagram of the pneumatic hookupcomprising an air motor with a two-hand con rol to illustrate a feature of the press. The parts are shown in open-press position. Since any suitable pneumatic controlmay be used with my invention, no claim is made herein to this par- I ticular motor means and control.

levera e mechanism, having greater efficiency than the conventional toggle leverageimparts final-heavy jaw compression to the work on the buck; and the motion is continuous from beginning to end,"thereby avoiding the two-step action so characteristic of conventional iv of twoicylinder presses.

Figurel is a side elevation of the press in wideopen position, with the pedestal frame in section presses, espetoexpose the press-operating mechanism, i. e.,

it leverage concealed therein. Sheet 2 including Figures 2, 3, 4 and 5 is'a motion study showing successive positionsof the press from beginning to end of its closing motion effected in one continuous stroke without a pause.

Figure 2 shows the press in wide-open position;

Figure 3 in mid-closed position; andFigure 4 shows it initially closed where the head is just "touching but not squeezing the padded'buck.

When it is noted that the head has swung through its long arc and reachedits initially-closed positionin Figure 4, it will then be appreciated that the stroke of the motor is only partly expended. Thus there remains a long portion of its power head from Figure 4 to Figure 5 position. der final ironing pressure, and by comparison with Figure 4 it will be observed that the padding on the lower buck is now under maximum compression.

Figure 5 shows the press stalled unage parts.

Figures 12 through 16 show the invention as further developed into a third form. Its fullthird form, in its new combination, permits the press to be operated at higher speed than the previous forms; consequently press operators can attain greater ironing production.

Figure 12 shows the third form of press wide open, and Figure 13 shows it fully closed. The hydraulic speed governor, by which it is now possible to increase the velocity of the ironing head, is not seen in these two views because it is mounted on the far side.

Figure 14 is a front View of the third form of the invention. The press is closed, and the front of the frame is broken away to expose the lever- Note the hydraulic governor on the right side of the press, and it is slightly enlarged driven by the latter, and a link of the toggle is 'fixed to that shaft. This hydraulic governor Figure 6 is a side view of the press in one of its more nearly commercial forms, with certain parts omitted for clarity, and showing a new crank-actuated spring-counterbalan-cing means for openingthe press}. and Figure '7 is a rear projection thereof, more'particularly made on the sectionline 1-7. These two views area development comprises a two-cylinder double-acting shock absorber and speed controller. Byits use here, in a new way, it is now feasible to close the ironing head at high velocity because the governor holds the leverage to its pro-adjusted speed and prevents the motor means from exceeding that speed. Also, the opening of the head can be acpressing head i l.

as the head-carrying arm oryoke I9 so that head-operating ,mechanism at the upper rear portion ofthe machine-so thatho danger exists in handling, or to persons who may be standing behind the machine while in operation, as during the operation, there are no moving parts projecting or kicking rearwardly during the opening and closing of the press. This part of the description is especially considered in connection with-Figures l; 8 and 9, inasmuch as it will be notedthat theseare side and rear views in several different positions. Thus is brought out the fact that maximum up and down travel of the two members it and S26 is accomplished without opening up a dangerous and unsightly operatingclearance space between them. In wide-open position (Figure 1), it is noted that the righthand clotted edge of the lever end 28 remains concealedwithin its embracinghead arm l9, 2|. This over or innerlapping of'side surfaces of the two relatively movable lever members [9 and 26 provides a shielding .means and thus fills the operating clearance 26 on both sides of the-arm and actuator assembly is, 26. This arrangement improves the solid. closed appearance and general safety of the machine. e

l In Figure 8 the upper end 25 of the actuating lever is purposely'shownin dotted lines behind the front tine 2i for clarity in illustration, but in actual manufacture the upper surface of the head-carrying arm .53 and its lever 26 may be made perfectly smooth and fiush'with each other to present a neat appearing design, wherein the "parts'rnerge by conforming to like or similar contour lines. My invention, therefore, takes into account not only safety, utility and simplicity, but also favors good appearance in the structural design of the press.

The compound-motion lever 25 extends vertically downwardly for a considerable distance and its lower extremity 28 is near the bottom of the press. When the press 'is open, the lower end 28 is substantially under the axis 22 of the When the press is closed (Figures 4, 5, 6, 3, 13 and 14), thelower lever end 28 is displaced outwardly from the pedestal frame 2, 3 to a positionnot further than occupied by the outer margin of the upper lever end 25 when the pre s is open (Figures 1, 2 and 12). 'this compact and vertically arranged operating assembly produces a pressing machine which may be installed close to the wall and occupies minimum floor space. r

The lower end 23 and central portion 25 of the lever curves inwardly toward the front 3 of the press frame to provide a projecting'bearing bracket or arm 29 oifset from the longitudinal axis of the lever. This oifset bearing arm 29 curves upwardly under and in front of the bearing bracket 9 when the press is open, providing for compactness in design and construction, and it is about one-third of the distance upwardly from the lower lever extremity 28. It will be forming a toggle-knee joint 33.

shown that the lever extension arm 29 is operatively connected with a variable-stroke high- .power heavy-pressure leverage, while the lower end 23 is operatively connected with a prime mover such as motor means or other actuator.

The motor will be shown to not only actuate the lever to first or initially close the press but also actuates the heavy-pressure leverage through said lever 25 without pause or interrupttion. The full movement from Figure 2 to Figure 5 position-is therefore a smooth continuous one performed by the simple low-power closing leverage i9, 25 which alone is not capable of imparting heavy ironing pressure to the head ll, although its leverage ratio is well suited for initially swinging'the head ll down to the buck it. As a matter of fact, the lower end 28 is seen to be only one-third the length of the upper end 25, taking the arm 29 as the fulcrum of the long lever 25.

two-thirds down, for bodily shiftable swinging motion relatively to the pres frame, upon a heavy pressure leverage of improved toggle formatiori comprising comparatively short upper and lower links 32 and 32. These two short links are pivotally connected together by a bearin pin The upper link 35 is carried by or pivoted upon a stationaryframe bearing 35 in bracket 9, while the other link 3'3 has its lower end connected with the forwardly extending lever arm 29 by a free or compound-motion pivot which follows the motion of the lever 25 in opening and closing the press.

The leverage ratioof the toggle 3!, 32 is suited only to the production of heavy ironing pressure; hence it referred to h rein as a high-ratio or a high-power leverage for the lack of a better name. Its force multiplyin amplitude is so great as to wholly unsuit it as a means for initially closing the press, a-function not requiring hi h power in the first place. A multiplication of the motive force, into a mechanical advantage stepped up or amplified many times, is only required going from Figure 4 to 5 position, and that amounts to a head movement of Qruy an inclrmore or less, whereas the travel from Figures 2 to 4 may be twenty times greater.

' In my experiments it' is found that the principle of my invention can be carried into effect with types and for-ms of low ratio lever mean other than that shown herein and indicated at !9, 25, and with high ratio lever means other than the characteristic toggle 35, 32 its equivalent fo cs shown'in Figures 8 and 12. At the same time, it is believed that the particular forms of the leverages, herein chosen to illustrate my invention and its principles, are also new and inventive.

The upper link 3! is integral with a counterbalancing arm 35 extending rearwardly from the frame bearing A press-opening or counterbalancing spring 3i has its upper end mounted on a pin 38 carried on the counterbalancing arm 35, while the lower spring end is attached to the press frame at 3%. It is often desirable in presses having large and heavy movable head to employ more than one spring 3? in order to increase the head-lifting force required to open the press. That is shown in the advanced views (Figures 6 and 7) but a single spring 31 is first shown to I of different thickness.

press. In other words, this member has a wide end 32 with close centers 33 and 35 in an upright plane, and has its long narrow end 4| extending therefrom a distance greater than the length of the upright link 32. The end 32 of the arm ll may he made in the form of 'a' fo rk to embrace the two parts 29 and 3E pivotally connected therewith. I I

The free end of theprojecting arm El is pivotally connected through a pivot 42 with one end of a short upright guide or a radius link 43. The latter in turn has its other end pivotally con; nected, through an adjustahl -frame bearing id, with the short of atoggle-adjusting lever, say a bell crank 45. Hence the radius link must swing on its pivot M, The bell crank is mounted inside the machine on a stationary-frame hearing il', with its other end extending along side the front frame upwardly. A handwheel d8 is journalled in the frame 3 and is fixed on a screw which is operatively threaded into the longer part of the toggle-adjusting lever 35. By turning the handwheel 58 one Way or the other, its screw runs in and out of a conventional swivel nut mounted in one arm of the bell crank 45 which moves the latter about its frame pivot ll.

The foregoingprovides for close or fine up and down movement of the adjustable-frame bearing it to adjust the arm ll around the compound-motion pivot 35 of the lever 25. Hence the heavy-pressure toggle Si, 32 isadjustable in relation to the press frame and hence the buck $5. The purpose thereof is to alter the relative angular positions of the three toggle hearings or axes 33, 3t, and 35, in relation to the upper pivot 21' of the swingable pull lever 25, by which to set the high-power leverage SI, 32 to apply more or less pressure between the coacting press jaws. While this adjustment is infrequently used, it is or may be provided for the purpose of setting or resetting the heavypressure leverage El, 32 so as to compensate for the variable factors which may arise when the padding i6 is changed, or more particularly when a pad of one thickness is replaced by one An actuating means co'mprisi g a fluid-pressure or pneumatic-motor means 50 is operatively connected with the lower end 28 of the lever to apply an angular force outwardly thereon and fulcrum the lever on its compound motion pivot 35 carried by the high-power leverage.

The cylinder 5% has one end mounted on a sta-' tionary-frame pivot 5| which permits its other end to oscillate and follow the motion of the lower end of the lever 25. A piston 52 with its connecting rod 53 is pivotally attached by a wrist pin 54 with the lever end 28. An air hose or tube 55 is connected with the head of the cylinder 5?) above the piston to supply air pressure thereto for forcing the piston in its power stroke rearwardly toclose the press. The air hose 55 is connected througha master valve 61 with a control manual hereinafter described.

When the piston 52 pushes outwardly on its power stroke, the lever 25 swings clockwise on its compound-motion pivot (traveling .ful-

crum) carried on the lower end of the heavypressure toggle 3E, 32. Consequently, the upper lever end 26 urges to theright, but the bearing pin 2? moves on "its are around the frame hear-- ing 22, and the head ll iscarried down by its arm '19. The lever 25 therefore swings clockwise on one pivot 35 and its lower end simultaneously swingoutwardly on its other pivotil, as demonstrated in Figures 2, 3 and l. That movement brings the pressing head llto its initially-closed position where the spring pad i5 resists furthermovement of thehead. At this point, there still remains a substantially long portion of the power stroke of the piston 52 (Figure liy I I The pressure flowing through the air hose rapidly builds up, so that the piston pushes to ward the outer end of the cylinder without a pause to Figure 5 position. The bearing pin 21 undergoes substantially a straight down but short movement from Figure 4 to Figure 5,

while the wrist pin fid pushes rearwardly a con siderable distance, and the toggle joint 33 moves toward adead center line defined by the pivot centers 3'4 and 35,hut doesnot pass therebeyond.

The link member 22, 4| initially acts (Figure 2 to Figure 4) as a means to carry and guide the' thrust link "35 and the traveling fulcrum 35 so that the actuating lever Eiirnay fulcrum clockwise on the pivot 35 to preliminarily close the press against the tension of the c'ounterhalancing spring 31; and thereafter (Figure 4 to Figure 5') the toggle Si, 82 more particularly functions as a heavy-pressure leverage by the straightening action of the toggle toward a straight line to produce a thrust through its straightening knee joint 33' while straightening to effect finale heavy jaw compression as the toggle links 3;] and 32 straighten to a point where the motor piston 52 stalls against the resistance of the buck l5. During preliminary closing, the upper 1in k 3l swings through a rather large angle (say about to degrees) on its frame pivot 35 since it is merely idling and not calledupon to exert a thrust, whereas during final movement" the link 31 swings througha smaller angle (say about 40 to 45 degrees) and thereby amplif es the force-applying function needed at that time to thrust and produce heavyjaw compression.

an all, the thrusting link 3| swings through an angular distance of a hundred degrees more or less, withoutits knee joint 3 3 passing dead center position. Inasmuch as the finalpressure movement of the head (Figure 4 to Figure 5) is through a short distance, a toggle formed of short links has its advantages; delivers greater thrust, and occupies less space. It is"unnecessary to havelong and cumbersome toggle links occupying considerable operatingspace when the initial closing or the press is not a power consuming operation of great magnitude and can toggle leverage as heretofore described, but in a more advanced form to more nearly show the principle of the" commercial construction, and

. more particularly to show a new crank-operating counterbalancing means to open the press. The same reference numbers are applied to the parts as heretofore described, except'for the additional,

companion or secondary elements now introduced' and explained. I l I The previously described arm' Bfihas a companion counterbalancing arm Eli which is also integral or fixed with the previously described short toggle link 3!, these threemembers taking the form of a fork, as shown (Figure 7) from the rear of the press. A companion spring 37 has its upper end attached to a pin 38* carried on the arm 35 and the lower end thereof is attached to the frame at 39*. The two counterbalancing arms 35 and 35% are made in the form of two spaced crankarmawith the bearing 9 mounted between 'them,and the frame bearing 34 acting 'as a crank bearing. The pins 38 and 38 for the two springs act as crank pins against which the springs exert a rotative force.

It is noted that the secondary crank arm 38 is shorter than the first arm 35. Furthermore,

, these two arms 36 and 36* are offset from each other a substantial angular distance or some 60 to 88 degrees, so the two springs 31 and S'l equalize each other and thereby do not work against the last portion of the power stroke of the motor (Figures 4 and 5) when the press is going under heavy pressure. Since the tension of the two springs 31 and SP is nearly the same, the longer crank arm 36 stretches the spring 37! to, apply a n" counter-clockwise torque somewhat greater than the shorter. spring 37 This double-spring counterbalance is built as an integral part into the heavy-pressure leverage 3 l, 32 and is efficient and smooth in its operation. This spring means acts directly upon the toggle joint 33 to collapse the links 3! and 32 and return them to normally open-press position when the air pressure i exhausted from the cylinder 55, thereby lifting the ironing head H to wide open position. Also, the

two crank arms 35 and 35* provide a method of installing multiple springs to open the press. Two sets oftwin springs are sometimes used, two parallel springs in position at 31 and two at 31 thus providing four springs. Multi counterbalancing springs are sometimespreferred so as to distribute the opening force among several springs to obtain an easier stretching action.

When the resistin spring padding to is under final ironing compression (Figure 5), a great reaction is. built up against the head ll. The spring padding it therefore aids in initiating the opening movement of the head ll when'the motor means 58 is deenergized and releases the thrustfrom the toggle Si, 32. The reaction in the spring padding it, with the tension of the spring means 31 and 37 quickly starts the opening movement of the press; After the crank pin .38 swings counter clockwise to the left of the crank bearing 34, it follows that the secondary spring 31 also applies torque around that bearing and aids the spring Bl in returning and holding the press to its wide-open position. v

. The guide link M possesses additional functions which impart an improved mode of operation to the heavy-pressure leverage 3i 32 which for convenience may be termed a toggle, although it functions wholly different from the conventional toggle. Another viewpoint is that the linkage SI, 32 may be termed a variablestroke crank and has been'thus called from time to time during the comparatively long period this invention has been under development. Whatever that may be, it is now explained that the element or projecting guide arm M itself constitutes a toggle control or'governor which, in its sequential action from Figures 2 to 5, acts to vary the stroke of the toggle or crank means 3|, 32. This reference to a variable-stroke crank means is made of course to the two short swing links 3! and 32 throughout Figures 1 to 7, and is not to be confused with the spring counterbalance crank arms 36 and 36? in Figures 6 and 7.

There is another toggle action to be noted and it likewise is controlled by the leverage variator means 4!, 43'. Reference is now made to pivots 21 and 3 By drawing a line through their centers it will be observed that pivot 35 does not pass that line when the press is under final pressure in Figure 5. The pivot 35 moves to the left rather rapidly, but the link ll continues to so reset and hasten the toggle joint 33 to the left as to rapidly increase the distance from the frame bearing 34 downto the compound-motion pivot 35 traveling downwardly, whereby the latter does not pass dead center defined by a line extended through the pivots 2? and 34. Consequently, what may be said to be an inverted togglellnk 25, is so arranged that it operatively depends from two pivots 2! and 35, the latter of which cannot look past dead center because of the amplitude variator 4!, 43.

Another feature of this invention is noted by study of Figure 5. Here the pres is exerting its maximum pressure and is standing under strain. The operating leverage mechanism and its pivots are not only compactly arranged for structural unity, but are so placedas to most effectively exert the pressure forces and expend same in compressing the. buck pad it. It will be observed that there are three pivots EL}, 22 and 21 lying within the arc of a circle which if extended pass approximately midway through the press jaws. In Figure 5, thecenter for a compass to draw this circular force path will be found by test to be slightly above and to the right of the reference number 9. This arrangement is found to be an advantage, in that the major portion of the pressure load sustained by the machine, while standing under final heavy pressure, is concentrated within a small space or area near the top of the machine adjacent the sturdy frame top or cover 6. The forces react and arch the circle in question and attain a static balance on the work being ironed between the press jaws by reason of the particular placement of the three main bearing points 34, 22 and 2?.

The thrust circle or power circle feature just described is further illustrated in Figure 13 where the reference number [2! also locates the center of the thrust circle passing through the center of the closed press jaws and through the three main bearings ill, 22 and 2?. Thus the major strain under which the press remains finally closed is carried by the frame top it and upstanding horns 5 which are integral and best qualified to carry such a load. Thus the lighter weight frame housing 2, 3 is not unduly stressed.

The high-power stationary cam-leverage shown in Figure 3 has its actuating end attached to the'lower end 28 .of the lever 25 by the wrist pin 5*5, while its upper end is attached to the top 6 of the press frame as shown. The spring is set at an angle to exert an upwardly forward pull on the lever 25 to raise the movable pressing head l1.

The motor mecas'ond its control A cam track 53 is held 'adjustablyEmounted on r a stationary-frame pivot 59. The cam track has a substantially vertical run (55 and a rear horizontal run 6i. A rollerfi2 is journalled upon'the compound-motion pivot or traveling fulcrum and is confined in the cam run to, E I for vertical and lateral travel therein The vertical cam run Bil supports and guides the lever while it fulcrums on its roller pivot 35 to exert an initial-closing force on the movable head 17.

An adjusting handwheel 63 and screw is adapted to thread in and out a swivelnut mounted in the end of the cam track 53 and is similar to the adjustment for the bell crank 5; The rear end of the horizontal run 5! of the cam tracl: is set downwardly by the handwheel to produce a down'pull on the lever 25. The cam run (it can be adjusted to compensate for the thickness of the buck pad to, and pressure between the coacting press jaws.

It is noted that the compound-motion pivot 35 in both forms (Figure-l and Figure 8) is adapted to undergo substantially the same an ular inovemerit. :iis comes about by reason of the fact that the lower lever end 28 first fulorums clock wise on its compound motion pivot 35, in either form of heavy-pressure leverage, to urge-forwardly against the upper pin El, whereupon said lever 25 starts downwardly (although still fulcruming on pivot 35) to complete the initial head-closing action, and finally its lower end endently swings far outwardly on its upper bearing pin 2?.

The foregoing newrnod'e of operation is an lefficlfiit one because the motor to first uses the upper. long lever arin (portion to above the arm 29 to attaina relatively fast closing speed. Thereafter a large ampiification of the force exerted bythe. lever is accompli, ted,

to regulate the final-heavy" greatly stepped up, by resolving its fulcrurning action on the pivot into an outwardly swinging motion, pendently, on'the upperpin 2?. That motion'of the lever is resolved into a downward pull exerted on the head arm Ed .by the cam runfil. l l a 1 The guiding orvariator linkage M, 3 heretofore explained, and the vertical cam run fiiihere discussed, alike performs a guiding function'io the lever 25 while it is'iulcruming on its pint .35 until the further travel of the head 51 is resisted the buckpaddinglld... Thereupon; the heavy-pressure toggle 3i, and the .zontal cam run (5!, alike exerta powerful down pull the lever 25 and its upper bearingzpin 2?, since the lever 25 no longer fulcrums on the pivot but swingspendently from the headcarrying arm 13 and shown at Figure 11" a This organization is shown in diagrammatic form, the motor means 56 thereofhaving been de scribed, The aforementioned air hose con- ,nccts with the central part of an automatic mas 'ter control valve body or housing El disposed in the lower part of the machine frame. A airfeed orpipe line 88, from a source of motive fluid or compressed connects directly with the top of the master valve 5?. After this master valve automatically opens, the compressed air, under full and unres ricted line pressure and volume ing through va;restricted manuahcor rol motorstarting valve means new 'briefiyexplained;

Any suitable pneumatic control may beius'ed pulls dovl nwardly thereon.

. motor as a ieature'oi this press.

the airhose into the cylinder. L

for startingthe motor means 5%! and initially closing the press (Figure i), and one example of such control is necessarily shown herein since it cooperates with a new automatic control for the A known form of two-hand control is selected as a motor-starting valve inorder to illustratethe feature inquestion. A left-hand button 66 is mount-ed at the front of the press table, while a right-handbutton H1 is spaced to the right thereof although not seen in the side view (Figure 1) since it is behind the button Edi The operator must depress both buttons 69 and 7d and hold them down with both hands to start the motor means and keep it energized until the pressing head. .l'l swings through the danger zone (Figure 3) and has reached the buck. (Figure 4) whereupon the oper ator safely releases both buttons. The master valve 6'. will be shown to then automatically keep the'motor in an energized state by holding open the mainair line E8 to maintain live air pressure on the piston 52. Doing so holds the press jaws sealed tight under compression and continues to urge the head H against yielding pad throughout the ironing operation. This is due to the fact thatafter the piston passes the port Bil. the air passes from the cylinder through the pipe and deflects thediaphragin upward holding the valve head 91 open.

:l'| which is the other two-hand. valve, and it-is operatedby the other button 78. The valve body .11 has a normally open exhaust valve with stem 18 adapted to be closed by the button Hi to shut an exhaust port l9 and thereby block oi? the tube lfi so that air flowing into he chamber of the master valve will not escape to atmosphere. In this way, the air pressure flowing downwardly through the tube 74 is directed upwardly through The button (it is depressed to thrust valve stem inwardly, this stem being common to a normally-closed intake-valve head 8! and a normally-open exhaust-valve head 82. 'Thataction reverses the valve unit PM, 82' against a spring 83 normally holding it in closed press position (Fig.- ure 11), so that the intake 3! is now open, the exhaust 82 is closed. Hence an exhaust port 84 is shut off from the branch 12, so that the latter opens directly into the air tube M connected with the valve body 13 between the opposed seats of the two Valve heads 8i and 82.

A throttling valve 85 is included in the branch tube 12 between the feed pipe 68 and the valve 13. This throttling valve 86 has a well known screw threaded needle valve or stem 8'? with a handwheel for adjusting it. The needle valve 81 can be screwed'in'and out to roguiate the size of the conventional port shown in the valve body 85 by which to restrict andregulatc the initial flow of air pressure from thelbranch tube l2 into the air tube T l and thence through the air hose 55 to the cylinder 5 to start the piston 52. The high-pressure air from the feed pipe through the pipes '12, M is preferably reduced by the hand valve 8'! in order to appropriately regulate the speed of the piston 52 and hence the closing action of the pressing. head H. The reducing An air tube it con-- 7 needle valve 81 is adjusted in accordance with conditions, such as the air pressure available in the 'feed pipe 58 and the personal desire of the operator.

On the other hand, full line pressure from the feed pipe 68 is desirable at the moment the head reaches the buck (Figure 4) so that no pause in movement occurs by reason of the resistance offered by the pad it. Quick and full line pressure compensates for the drop in pressure in the cylinder 56, occasioned byithe rapid outstroke of thepiston 52, and prevents the piston from hesitating when the head first meets the resistance of the pad. 7

The operator depresses both buttons 59 and i6 and starts the motor piston 52 on its outer stroke toward aport 89 which is not uncovered by the piston 52 until the head i'lhas passed through V a the. danger zone and reaches its initially-closed (Figure 4) position. It will be borne in mind that the push button 69, when depressed, opens the normally closed intake valve head Bi and closes the normally open exhaust valve head 32, and that the push button 10, when depressed,

. closes a normally open exhaust valve, and also that the'relea'se lever 99 when operated, opens a normally closed exhaust valve head H39, which exhausts the air from the diaphragm chamber 9!, permitting the valve 94 to return to its nor-' mal position, wherein the head 97. is closed. When the port 89 is uncovered by the piston 52, the air pressure in the cylinder then flows through a diaphragm-feed hose 99 into a. housing 9i and deflects a diaphragm 92 upwardly. The diaphragm Q2 pushes on a stem 93 to close a master-exhaust valve 94 against its seat 95.

The upward movement of this valve 94 in'turn pushes on a stem 96 and opens a normally-closed I master-intake valve 91,

7 Air pressure now by-passes the branch '52 and flows directly from the feed pipe 68 past the open intake 9'! and into the air hose 55, Inasmuch as 95. The thrust of the diaphragm'fifi, however, r is adequate to compress the spring 98 and thereby reverse this unit-valve setting from Figurell position when the piston 52 uncovers the cylinder port 89. r The spring 98 restores the master valve A simple form of press-opening trigger-release manual 99 is mounted on the table, say on the front flange 7 thereof conveniently under the two-hand control valves 69 and 10. This trigger release 'fid may be pivoted on a valve body IElE! having'a large exhaust port iD| normally closed by an exhaust valve head with stem :02. A spring keeps the valve I62 seated to normally close the exhaust port [6| and keep the trigger $9 in down position. This press-opening exhaust valve lEiEi is connected through an exhaust tube 33 with the diaphragm chamber 9i.

,By lifting the trigger 99, the valve 592 is thrust inwardly against the seating pressure of the spring shown, and the large exhaust port lill instantly vents the diaphragm chamber 9| to at,- mosphere through the tube N13. The outlet through the exhaust port ||l| is somewhat larger than the cylinder port 89, so that a drop in pressure instantly occurs in the diaphragm chamber 9| whenthe trigger 99 is lifted. The master valve spring 98 then snaps the intake valve. 9'! closed and exhaust valve 9 3 open (Figure 11 position) with the result that the air from the cylinder 5G rapidly exhausts back through the air hose 55 and out through the exhaust tube 76 and port '59 in the valve body ll. The springs 31 and 3% then open the press as heretofore explained. Briefly upon depression of both push buttons 69, it; air passes from the main line 68 through pipe 72 and pressure reducing valve therein, to valve casing "i3, past'the open intake valve head 8|, through pipe "is, to the valve casing 61, thence through pipe 55 to the cylinder 59, actuating the piston therein on its power stroke. Because the valve head operated by the push button 16 is closed, the air can not exhaust out through the pipe 'iii'from the valve casing 67. The air can a not pass from the main pipe 68 to'the cylinder,

because the valve 9? is closed. When the piston 52 on its power stroke passes the port 89, the airthen passes from the cylinder through pipe 96 into the diaphragm chamber 3i actuating the diaphragm 92 to close valve head 94 against its seat 95 and open valve head 96 so that now air can flow from the pipe 68 past the open valve head 53'! and through pipe 55 to the cylinder. The air can not exhaust from the pipe 96 out through pipe m3 and release valve I00 because the valve head in the casing we is closed. Thus because of the reducing valve 86, the press moves toward closed position under reduced air pressure but means to open-press position as shown, and deflects the diaphragm Q2 downwardly when the pressure is relieved from'the diaphragm chamber 9|, and thereby deenergizes the motor 50, the means for which will now'be described. 7

The cylinder port 89, in conjunction with the master valve 61, by-passes or cuts'out the motorstarting branch line I2, M with its throttling valve 36 and two-hand control valve 13, doing so i just as the pressing head ll meets the resistance of the padded buck l5, IS. The then instant application of full air flow, unrestricted as to volume and pressure, coming directly from the feed pipe' SS, raises the pressure to the cylinder so asto continue the power stroke of the piston.

goes under final pressure under full or heavy air pressure. Operating of the release valve lever 99 to open the exhausttvalve head in the casing I Bil exhausts the pressure from the diaphragm 9|,

permitting the valve head 9i to close and cut off the air pressure; and as the operator has some (iii time previously released the buttons 69, it, the valves operated thereby are in their normal position. Thus the operator holds the push buttons 69, lb depressed until the piston passes the port 8% at which time'the button 69 can be released and the press'will remain closed, due to the air pressure in the diaphragm chamber 9i. It will remain closed until the release lever 99 is open.

Thesiuinging-cam high-power leverage with its oarz'ator and hydraulic speed governor shown in Figures 12 thru 16 frame and, because it is cam controlled possesses an improved mode of operation over its predecessor-1 H in the previousviews. This cam-type leverage variatorIIS so modifies or guides the action of the toggle links H2 andIZIG as to producea new element in full-automatic pressing machine leverages. It may be said that alone the two operating links'II'2 and H8 comprise a toggle, but this coupled-in variator control member I I8 is believed to not only make thereof a new toggle per "se, but also constitutes a new combination. Thus, either ,variator II or IIB, coupled into the links I I 2 and I It, forms a toggle wholly different from the generally accepted form. Insofar as itis structurally and operatively known and understood, aside from the mere names of'these parts, singly or in combination, this new. arrangement affords a marked improvement in laundry-press leverages.

.It will be seen that the leverage-variator itself is made integral withthe link H6, but for convenience one number points to its left end as the coupling portion IIB between the pivots IM and H5, while another numberv H8 points to the right-hand end as the leverage governor portion having an automatic stroke-regulating and controlling action over high-power toggle IIZ, I I 6 as wel1 as the stroke motor piston 53.

Thefleverage variator II8 has formed in its outerxor forward. end a long. downwardly sloping press-closing. cam-run H9. which joins a short upwardly sloping heavy-pressure cam-run I26. The latter portion I26 is more nearly horizontal when the press is open'(Figure 12 but assumes an up-turned position (Figure 13) when the pressis closed. The press-closing cam-run'I Id and the. heavy-pressure cam-run I29 are joined by a'cam-turn I2I. The first and longer camrun I I9, from'its upper left end down to the turn IZI, 'is'defined by a radial curve, the center of which is located just beyond the lower edge of the member H8. At the same time, the second and shorter cam-run I23 is defined'by a shorter radial curve, extending upwardly and to the right, the center of which is just beyond the upper edge of the member I I8. The two cam curvatures appear here in small scale, but become morepronounced in'larger scale and when observed .in the full-size machineJ The leverage variator or differential-cam arm .IIS'is confined on .a cam rollerIZZ journalled upon the-bell crank heretofore numbered #35, but I now indicated at I23 in Figures 12 and The roller. I22 functions a frame bearing since it is held in a stationary position by the bell crank lever I23 adjustably anchored tothe press frame. This lever is. pivoted on the inside front of the press. at I24 by the frame bracket It]. One end mounts the cam roller I22 and its other end is susceptible-to a limited adjusting movement about the frame pivot I 24 for the purpose of varying'th'e up and down position of the cam roller I 22. This adjustment is preferably used only by the manufacturer of this press for properly setting its ironing head and the heavypressure leverage to a predetermined position closely gaugedand checked after the press is assembled and the padding Ifiis in place on the buck." .Such' adjustment once made is permanently fixed and remains in that position after the presses gointo service unless maladjusted by inexperiencedhands. a

The upperend of the bell crank lever I23 is shown as provided with anysuitable means for adjustably anchoring it to;'the frame and for making the above explained adjustment at the factory. One convenient device for this may be a fork at the upper end of the bell crank to receive a swivel nut I25, into which is screwed an adjusting bolt I26 having'a lock nut on the outside of the press frame 3 and a collar: fixed to this headed bolt I26 on the inside thereof. After the press is assembledand the pad I5 is installed, a wrench is used on the bolt I26 and its lock nut for the purpose of very finely setting the hell crank I23 about its frame pivot I 24. Thus the position of cam roller I22 is carefully adjusted up or down so that it correspondingly moves the front. end of the leverage variator I I8, and hence moves the motion-transmitting means 25, ie in terconnected' between .the'motor 5i] and head Il, to apply that predetermined ironing compression between the head and buck as best suited for the particular type and modelof press when itgoes into service; s

The above-described adjustment to attain the requisite ironing pressure is set into'the machine atthe factory as a part of its construction and is inherent therein. The purchaser or user of the press is not required to manipulate the device I26 or. changeits adjustment as originally made on the machine by a factory expert. .The adjustment hand-wheelllB shown in the previous views is for the same "purpose'but it is found that through mistaken impression some operators may get this new press out of adjustment by turning the conveniently arranged handwheel 53. So it is'found at one time preferable to remove it and substitute this smaller adjustment screw head I25 which, being up under the table of the press and not a convenient handwheel, is not seen. and is not so readily adjustablelbya curious operator, and is less likely to be tampered with. On the other hand, some users are not satisfied unless they can adjust their press, so thatin the end a fairly accessible hand-adjusting meansmay be better.

In coming to the description of some of the operating characteristicsof this new press, reference may be made to previous views, particularly Figures 2 toe showing a motion study. It is seen that the roller I22 is normally at rest adjacent the cam-turn IZI when the press is open (Figurel2) and lies within the long camrunIIQ. When air pressure is admitted to the front end of the cylinder 50, the lower end 23 of themain lever 25then tilts rearwardly'on its pivot or II5.

Now the ironing head I? starts downwardly around its pivot center ,22, thus forcing the fulcrum point H5 downwardly, and the head-closing cam-run I i9 first runs downwardly to the right on the roller I22 for the major travel (Figures 2 to 4) of the head I 1 towards the buck pad I 6. 'During that travel, the action of the first cam-run H9 rapidly shifts the toggle joint I It clockwise to the left (and thus runs or advances this center pivot or toggle joint Ila'in between the outer pivots III and H5) and thereby differentially increases (steps up) the amplitude or stroke of the leverage or crank means IE2 and H6 acting at this time (Figures 2 to l) as a mere guide for the lever 25. In other words, the low-power lever 25 is carrying with it the high-power leverage H2, II 6, and the leverage variator I I 8 is accelerating the traveling fulcrum M5 by reason of the progressive decrease of the mechanical advantage of the low-power leverage I9, 25 which hastens the head-closing motion and economizes on the stroke of the piston 52.

streams joint i it is advanced to theleft (note'the same pivot 32 in Figure 2) over thepivot H5, thereby pushing downwardly on the latter,.and drawing downwardlyon the'lever 25 and head 11, doing so without undue expenditure of-themotor piston stroke. i Just before the short link H2 reaches its down position (Figure 13) itibegins to amplify the power of the motor means'52 and; apply vfinal pressure before its stop H3 reaches the frame shoulder stop i It. This is due to the fact that the ironing head IT has reached its heavy pressure position and the motor piston 52 has stalled by reason of the resistance of the buck padding it. When the head reaches the buck (Figure 4), the leverage variator H8 reverses and acts somewhat the same'as link'fl (compare its Figure 4 positionto Figure 3)"'and now travels reversely upwardly to the left until the cam-turn Hi this time comes all the way back to the roller I22, at which position the ironing head is taking up the softness or fluffy slack in the spring padding IE.

roller E22 (goes around the'corner) and the second camrun lZil travels slowly-to the left and i downwardly onthe roller while thehi'gh-power leverage H2, H8 is urging the'he'ad from Figure 7 4 to Figure 5 positibn into ifinal-jaw compression.

7 The piston 52 finally stallsunder power, but

maintains its forceful urge on the head 11' to inch it downfor any give'in the padding 16. However, the toggle-stop meanslHl, H3 do not yet engage sinceit is preferred that the link H2 remain free to urge clockwise as the motor piston 52 urges the head tighter on the buck pad 16.

At the inceptionofhead-rnotion, that is, in starting the head ll dov'vnwa'rdl'yb-y overcoming its inertiath'emotor 5!! uses lts first powerimpulse to directly-fulcrum the low-power lever enough to stretch the counter-balancing springs or M25 is all that is required. x The high-power leverage 3|, 32'as well as H2, lihatthe start of the motor piston 52 and while the head is swinging toward the lpuck (Figures? to i), does not resist the thrust of the piston but merely idles and follows E downwardly with the lever 25. Thus thelinotive forceap plied at thewrist pin it acts directly tofulcrum the lcver25'up0n the pivot 35or1 5, to efiect the long head-closing motion, and the high-power leverage during wartime (Figures'2 to 4) acts to accelerate the down motion ofthelever, 25'and decelerate the stroke of thepistontgflso as to conserve the latter untilthe end, that (Figures a to 5) for compressing the padding" it under final ironing pressure." Easier and less sudden head startin is now attained withthi s motiontransmitting means, in the form of a new compound leverage," thanin conventional laundry presses having a. single-cylinder operatively cori- The cam-turn l2! now actually traverses the thick.

nected with the lhigh p'ower side of a compound leverage V i When'the press first starts closing, the camrun H9 runs downto the right on the. roller 122' and the outer free e'ndof the leverage variator H8 swings counter-clockwise on theroller, but

by the time the head reaches the buck (Figure 4:) v the first cam-run has reversed its direction and returned the cam-turn Hi to the roller. 1 vAs the cam-turn I21 now goes around and past the roller, the ironing head begins to go under compression against the pad [6, and the outer and short cam-run I20 so controls and'works with the decelerating leverage H2, H6 that the piston 52 of the motor now increases the length of its stroke proportionately over the reduced down travel of the fulcrum as to impart a short movement at a reduced leverage ratio to the ironinghead due to the straightening movement of the toggle links H2, H6 during the compara tively long travel of the piston 52.

The camand roller means I22 sustain a small proportion of the total bearing load or thrust and are not subject to the considerable wear and tear experienced with conventional presses having direct-acting cam leverages. Only a small fractional part of the total load carried by the high-power leverage H2, H6 is transmitted to the cam run and roller I22. Minimumwearocours and the mechanism gains increased life.

I Either of the leverage variators 4! or l8 pays out the stroke of the piston 52 very sparingly,

. from just after the head H is started, on through Figure 3 and to Figure e-position. Thus the variator H8 saves back the power stroke of the motor piston 52 until Figures position, whereupon the second cam-run S20 pays out very rap,- idly on the piston stroke. This action, of course, could notbe attained by employing an ordinary toggle linkage, but is very largely accomplished by tlierestricted'or captive link regulating the movement of the leveragevariator ll in the first form of this invention, and now more efficiently accomplished to a nice degree bythe contour of the cam-runs I it and mi in'the new leverage variator I it. In short, the cam slot H9 1 and follower 01' pin. 22 bring about approximately the same movements ofthe arm H3 and the toggle links H2 and H6 (Figure 12) as the link 43.brings about in the arm 4! and togglelinks 53!, 32 (Figure l). V

When the spring padding Iii on-the buck wears down thin and loses some of its resiliency, this press produces the same ironing compression as when the padding is new and flufiy and possesses itsoriginal resiliency. This is accomplished by the follow-up stroke of the piston 52 and the action of theccmpound leverage with its variator M or H8. Also, there is no toggle locking (over centering) action during any stage of pad wear, and for the; thinnest worn p'adthere always remains enough piston stroke to deliver the same ,iaw compression as when the pad is new and The pad.l6' wi1l recedeunderhardusageand lose its resiliency and thicknesshut this leverage follows up (or here it'follows down) that pad recession by urging the head i! downwardly for" any fractional diminishing of the original thickness of the pad. Consequently; this new compound leverage, actuated by a single motor mean-s, producesuniform pressure and uniform ironing quality for all degrees of thickness of the padding It. A new pad of the same make, thick ness, and constructioncan be installed by the condition.

operator on the press without altering the adjustment device 48 (Figure 1) or I26 (Figures 12 and 18). However, if the press user or operator 'puts' on another typ of pad, not conforming to thestandard factory pad, then the adjusting lever .45;or I23 must be reset-to this new padding When the air pressureis exhausted from the cylinder 5B,.the:reaction and expansionof the spring padding I6 impartsan opening impulse to the press. Bothc'ounterbalancing springs 37 and I 65 then readily act to carry either pivot or I I5 in a counter-clockwise return motion to open the press. This is true for any relative position of the ironing head from Figure 4 to Figure 5, and for any degree of pad wear and recession. a In the installation of a new pad 16 on the buck, as well as for other purposes of convenience, the toggle stop means IIli, IE3 merely prevents the toggle knee joint H4 from accidentally snapping too far to-theleft (Figure 13). The

powerlof'th press-opening spring I65, Or other.

forces, might accidentally throw the'toggle joint II4 so far beyond its normal travel as to make it hard to'bring it back, and since that might occur when servicing or repairing the machine, the toggle stop I I 0, I I3 is provided as a means to forestall that difficulty. The press leverage withits built-in hydraulic governor shown in Figures 14, 15 and 16 In order to control the speed of the ironing head I7, and in particular render it possible to swing the head up and down at high velocity, without shock and strain upon the press, a combination speed controller and shock absorber is operatively connected in a direct manner with.

the press leverage in a new and efiicient way. Ordinarily, I call this device the hydraulic governor for thepress, and its two functions are believed to be accomplished by animproved mode of operation over conventional laundry-press practice. The construction of the hydraulic governor constitutes the subject matter of divisional application Serial Number 338,785, filed June 4, 1940.v J

It isto be noted, in the examples shown, that the hydraulic governor is directly connected to the main shaft carrying the high-power leverage, say the shaft 34 (Figures 1-7) or the shaft III (Figures 12-14) where, in these latter views,

thehydraulic governor is now referred to and described. Consequently, the swinging toggle link 3i is to be fixed to the shaft34 to rock it, and likewise the toggle link I i2 or pinned at I 29 to the high-power leverage shaft I H to drive or rock the latter'as an actuatingmedium for a hydraulic governor I39 now described. .:The high-power leverageshaft 34 or III has a large degree of rocking motion. Y The swinging action of the high-power toggle leverage 3I, 32 or II 2, H6 acts to positively rock the shaft 34 or I II within the frame bearings 3 or I68 as a power shaft to drive the governor I30. The shaft .III is rocked clockwise by the motor piston 52 to close the ironing head H, and it. isreversely rocked counter-clockwise by the counterbalancing spring means I85 to open the press. "It is important to-note that the shaft III is directly coupled to the hydraulic governor and it, also acts to permit maximum opening is shown keyed 4 a teeny shifting speed but checks the momentum of the latter and absorbs the'shock at the end of the fastopening cycle- Th hydraulic governor includes a stationary cylinder or block I30 mounted on the side of the press frame, as by screws.I32 threading into bosses I33, pinion'shaft I34 journalled in the upper part of. the cylinder block I36 in position to come into alinement with the shaft III or I34. The shaft J34 has a coupling head I35 which mates with the coupling head I36 on the shaft iII of the press. On the shaft I34 within the cylinder block I30 is mounted a pinion I38, this being located just beneath the cover I3I for the cylinder block.- Thepinion I38 meshes on opposite sides of its axis with racks provided on piston plungers which work in bores in the cylinder block I39. One of these plungers I39 is provided with'a piston head .I4I working in the cylinder I 40 within the cylinder block I30. The other plunger I is provided with a piston head M6 working in another cylinder bore I47. During therockingof the pinion I38, these plungers move in opposite directions relatively to each other. Suitable valves are located to control the flow of fluid into and out of the lower end of the cylinders from and to the interior of the cylinder block I30 which constitutes a reservoir. M2 designate the valve casings. These valve casings also carry adjustable throttle pins I 43 and M8 respectively. As thesubject matter of this hydraulic check forms no'part of this invention but constitutes the subject matter of another application, it is sufiicient to bear in mind, in so far as this invention is concerned, that the opening and closing movement of the press is governed by this hydraulic check through a high power shaft of the press mechanism, as the shaft II|..

xIn the operation and use of the press, the operator makes her lay of the damp laundered apparel or work piece upon the buck It in the usual way and then depresses the control buttons 69 and ID (Figures land 11) as previously explained, to energizethemotor and close thepress. Any suitable form of motor means and control therefor can of course be employed in connection with thevarious features of this invention, so the air motor and its control are merely-referred to. here in an illustrative. sense. The ironing head I! remains under final heavy jaw. compression; until the work is ironed dry, whereupon the operator causes the press to open by any'suitableopening control, as indicated at 99 (Figuresl and 11).

In operation, the motor 50 delivers an outward thrust on the lower end 28 of the lever 25 which initially pivots the lever clockwise on the travelling fulcrum II 5. This motion imparts a forward and down motion to the head arm pivot 21, with the result that the lever 25 undergoes movement downwardly and clockwise, and at the same time begins to straighten the high-power toggle leverage II 2, I I6. As the 'latter straightens, the leverage variator II8 functions as previously explained to accelerate the downward motion of the travelling fulcrum H5 and in turn decelerates the stroke of the piston 52, thereby saving back part of the length of the latter for applying the greater force needed in going under final pressure (Figures 4 to 5).,

Thus the motor means 50, or other form of actuator, initially acts directly upon the lowpower leverage I9, 25 to swing the ironing head 

